EP3798451A1 - Propeller fan and air conditioner outdoor unit provided with propeller fan - Google Patents
Propeller fan and air conditioner outdoor unit provided with propeller fan Download PDFInfo
- Publication number
- EP3798451A1 EP3798451A1 EP19810828.4A EP19810828A EP3798451A1 EP 3798451 A1 EP3798451 A1 EP 3798451A1 EP 19810828 A EP19810828 A EP 19810828A EP 3798451 A1 EP3798451 A1 EP 3798451A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- blades
- propeller fan
- axial line
- roots
- blade
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/32—Rotors specially for elastic fluids for axial flow pumps
- F04D29/38—Blades
- F04D29/384—Blades characterised by form
- F04D29/386—Skewed blades
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0018—Indoor units, e.g. fan coil units characterised by fans
- F24F1/0029—Axial fans
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
- F24F1/38—Fan details of outdoor units, e.g. bell-mouth shaped inlets or fan mountings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2240/00—Components
- F05D2240/20—Rotors
- F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
- F05D2240/303—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor related to the leading edge of a rotor blade
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2240/00—Components
- F05D2240/20—Rotors
- F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
- F05D2240/304—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor related to the trailing edge of a rotor blade
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2240/00—Components
- F05D2240/20—Rotors
- F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
- F05D2240/307—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor related to the tip of a rotor blade
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2250/00—Geometry
- F05D2250/90—Variable geometry
Definitions
- the present invention relates to a propeller fan and an outdoor unit for an air conditioner provided with the same.
- propeller fans are used to blow air to outdoor heat exchangers.
- an outdoor heat exchanger is disposed on a side upstream of a propeller fan in an outdoor device of an air conditioner, it is not possible to cover a leading edge side of blades with a bellmouth due for a reason of disposition of the outdoor heat exchanger, and a configuration in which only a trailing edge side of the blades is covered with the bellmouth is employed.
- design of the propeller fan alone that is, design that takes only the flow in the axial line direction into consideration does not lead to input reduction or noise reduction since the practical flow field is not taken into consideration, and it is thus not possible to sufficiently improve performance of the propeller fan.
- the present invention was made in view of such circumstances, and an object thereof is to provide a propeller fan capable of improving performance and an outdoor unit for an air conditioner provided with the same.
- a propeller fan includes: a shaft portion that rotates around a center axial line; and a plurality of blades that have roots connected to an outer periphery of the shaft portion and extend in a radial direction, the blades have trailing edge side surface area increased regions and leading edge side surface area increased regions such that dimensions in an axial line direction parallel to the center axial line are larger on a side of tips than on a side of the roots in a case in which the blades are projected to a meridional plane including the center axial line, and the trailing edge side surface area increased regions are larger than the leading edge side surface area increased regions.
- the trailing edge side surface area increased regions are set to be larger than the leading edge side surface area increased regions to cause the trailing edge side to work more, and a flow in the radial direction is thus suppressed in the trailing edge side surface area increased regions. It is thus possible to curb peeling of a fluid from suction surfaces of the blades on the side of the roots, to uniformize flow amount distribution in a blade height direction (radial direction), and thereby to improve performance.
- solidity obtained by dividing a chord length of the blades by a pitch is equal to or greater than 0.5 and equal to or less than 1.0, and is preferably equal to or greater than 0.6 and equal to or less than 0.95. Further, the solidity preferably reaches a minimum value at a midpoint position of the blade height.
- a deflection angle obtained by subtracting an outlet angle from an inlet angle is set to substantially linearly decrease from the side of the roots to the side of the tips of the blades, for example.
- the dimension of the blades in the axial direction in a case in which the blades are projected to a meridional plane is set to be substantially constant from the roots (blade height ratio of 0%) to a blade height ratio of about 35% and substantially linear increase from the blade height ratio of about 35% to the tips (blade height ratio of 100%) .
- a blade stagger angle of the blades with respect to a direction of the center axial line locally increases such that an amount of change from distribution that substantially linearly increases from the side of the roots to the side of the tips has a maximum value at a center position of a blade height with reference to the distribution.
- the stagger angle of the blades is increased, that is, if the blades are caused to rotate such that the shortest distance from a leading edge and a trailing edge of a blade to an adjacent blade becomes short, the blades are directed in a direction in which the blades do not work, and the pressure thus decreases. It is possible to optimize pressure distribution on the surfaces of the blades in the radial direction, to reduce required input to the propeller fan, and thereby to improve performance by locally increasing the blade stagger angle such that the amount of change from the distribution that substantially linearly increases from the side of the roots to the side of the tips of the blades has a maximum value at the center position of the blade height with reference to the distribution.
- a propeller fan includes: a shaft portion that rotates about a center axial line; and a plurality of blades that have roots connected to an outer periphery of the shaft portion and extend in a radial direction, a stagger angle of the blades with respect to a direction of the center axial line locally increases such that an amount of change from distribution that substantially linearly increases from a side of the roots toward a side of tips of the blades has a maximum value at a center position of a blade height with reference to the distribution.
- the stagger angle of the blades is increased, that is, if the blades are caused to rotate such that the shortest distance from a leading edge and a trailing edge of a blade to an adjacent blade becomes short, the blades are directed in a direction in which the blades do not work, and the pressure thus decreases. It is possible to optimize pressure distribution on the surfaces of the blades in the radial direction, to reduce required input to the propeller fan, and thereby to improve performance by locally increasing the blade stagger angle such that the amount of change from the distribution that substantially linearly increases from the side of the roots to the side of the tips of the blades has a maximum value at the center position of the blade height with reference to the distribution.
- an outdoor unit for an air conditioner includes: the propeller fan according to any of the aforementioned propeller fans; a heat exchanger that is provided on a side upstream of the propeller fan; and a bellmouth that is provided so as to cause a leading edge side to be exposed and cover a trailing edge side of the propeller fan.
- Fig. 1 illustrates a sectional view of an outdoor unit 1 for an air conditioner (hereinafter, simply referred to as an "outdoor unit 1") in a side view.
- the outdoor unit 1 is connected to one or a plurality of indoor units (not illustrated) with a refrigerant pipe.
- a propeller fan 5 is disposed in a casing 3 of the outdoor unit 1.
- the casing 3 has a substantially rectangular parallelepiped shape standing on a leg portion 4 placed on a floor surface.
- the propeller fan 5 is rotated about a center axial line L1 by a motor 7. Since the center axial line L1 extends in the horizontal direction, the propeller fan 5 transversely blows air and causes the air to flow in the horizontal direction.
- the propeller fan 5 has a shaft portion 6 that is connected to the motor 7, is located on the side of the center axial line L1, and serves as a hub and three blades 8 that are secured to an outer peripheral surface of the shaft portion 6. Note that the number of blades 8 may be two, four, or more. The blades 8 extend outward in the radial direction from roots 8a connected to the shaft portion 6 toward tips 8b.
- An outdoor heat exchanger 9 is disposed on a side (the right side in the drawing) upstream of the air flow of the propeller fan 5.
- a bellmouth 10 is disposed on a side (the left side in the drawing) downstream of the air flow of the propeller fan 5.
- the bellmouth 10 is provided so as not to be present in the surroundings of a leading edge side 5a of the propeller fan 5 and to cover the surroundings of a trailing edge side 5b of the propeller fan 5. Such disposition in which the leading edge side 5a of the propeller fan 5 is exposed from the bellmouth 10 is employed.
- Fig. 2 illustrates a vertical sectional view of the outdoor unit 1 in Fig. 1 in a plan view.
- the outdoor heat exchanger 9 is provided from a left side surface 3a on one side to a back surface 3b of the casing 3 and has a shape folded into an L shape. Since such an outdoor heat exchanger 9 with the L shape is employed, an air flow passing through the outdoor heat exchanger 9 and flowing into the propeller fan 5 forms a complicated flow field.
- a machine chamber 12 in which a compressor that compresses a refrigerant and the like are disposed is provided on the side of the right side surface 3c of the casing 3.
- the machine chamber 12 and a space in which the air flows due to the propeller fan 5 are sectioned by the sectioning wall 14.
- Fig. 3 illustrates a front view of the propeller fan 5 when seen in a direction of the center axial line L1.
- the counterclockwise direction corresponds to a rotation direction R.
- Leading edges 8c and trailing edges 8d of the blades 8 have such shapes that the blades further stick out on the side of the tips 8b than on the side of the roots 8a.
- the blades 8 have a sickle shape in which the leading edges 8c are inclined forward in the rotation direction R.
- Solidity ⁇ of the blades 8 is equal to or greater than 0.5 and equal to or less than 1.0 and is preferably equal to or greater than 0.6 and equal to or less than 0.95. Also, the solidity ⁇ reaches the minimum value at a midpoint position of the blade height.
- an inclination angle of the leading edges 8c with respect to the direction of the center axial line L1 is an inlet angle ⁇ 1
- an inclination angle of the trailing edges 8d with respect to the direction of the center axial line L1 is an outlet angle ⁇ 2, as illustrated in the drawing.
- the horizontal axis represents the blade height ratio while the vertical axis represents the deflection angle ⁇ .
- the blade height ratio is 0 (0%) at the roots 8a and is 1.0 (100%) at the tips 8b (the dimension of the direction of the center axial line L1).
- the dimension of the blades 8 in the direction of the center axial line L1 in a case in which the blades 8 are projected to a meridional plane is set so as to be substantially constant from the roots 8a (blade height ratio of 0%) to the blade height ratio of about 35% and to substantially linearly increase from the blade height ratio of about 35% to the tips (blade height ratio of 100%).
- the horizontal axis represents the blade height ratio while the vertical axis represents the axial width expressed in a non-dimensional manner with the diameter at the tips 8b of the blades 8.
- Fig. 7 illustrates distribution of the leading edges 8c and the trailing edges 8d of the blades 8 in a case in which the blades 8 are projected to a meridional plane, in the radial direction (horizontal axis) and the axial direction (vertical axis).
- the axial width is larger on the side of the tips 8b than on the side of the roots 8a of the blades 8 as illustrated in Fig. 6 .
- Regions (leading edge side surface area increased regions S1) sticking on the side (the lower side in the drawing) upstream of the air flow is present from the side of the roots 8a at which the position of the leading edges 8c in the axial direction is constant to the side of the tips 8b.
- regions (trailing edge side surface area increased regions S2) sticking on the side (the upper side in the drawing) downstream of the air flow is present from the side of the roots 8a at which the position of the trailing edges 8d in the axial direction is constant to the side of the tips 8b.
- the trailing edge side surface area increased regions S2 are set to be larger than the leading edge side surface area increased regions S1 (S2 > S1).
- the trailing edge side surface area increased regions S2 are set to be larger than the leading edge side surface area increased regions S1, the side of the trailing edges 8d is caused to work more, and the flow in the radial direction is thus suppressed in the trailing edge side surface area increased regions S2.
- Figs. 9 and 10 illustrate a simulation result of the present embodiment.
- the simulation was conducted under a condition of a positional relationship among the propeller fan 5, the outdoor heat exchanger 9, and the bell mouth 10 as illustrated in Figs. 1 and 2 . In other words, this is not a simulation result of the propeller fan 5 alone.
- the rotation direction R of the blades 8 in Figs. 9 and 10 is clockwise turning (right turning) unlike in Fig. 3 .
- Fig. 9 is a simulation result of a typical propeller fan in a comparative example.
- limit streamlines illustrated on the suction surfaces of the blades 8 are directed in the radial direction.
- the radial direction component of the limit streamlines illustrated on the suction surfaces of the blades 8 are reduced, and the limit streamlines are in the direction that substantially follows the rotation direction R, as illustrated in Fig. 10 .
- a second embodiment of the present invention will be described.
- the present embodiment was achieved by partially changing the shape of the blades in the first embodiment.
- description of matters that are common to those in the first embodiment will be omitted.
- a blade stagger angle ⁇ 1 is an angle formed between a tangential line L2 that is in contact with each blade 8 cut at a predetermined position in the blade height direction on the side of the pressure surface (front surface side) and the direction of the center axial line L1.
- an intersection between a line connecting a gravity center of the blade 8 to the center axial line L1 with a shortest distance and a blade sectional surface cut at a predetermined position in the blade height direction was defined as a center position A, and performance in a case in which the blade stagger angle ⁇ 1 was changed by causing the blades 8 to rotate about the center position A was compared.
- Fig. 11 illustrates a case in which the blades are caused to rotate at the position of the blade height ratio of 25% to change the blade attachment angle ⁇ 1.
- the horizontal axis represents the rotation angle of the blades 8 around the center position A while the vertical axis represents an input ratio of the blades 8, that is, a value obtained by dividing a power required to cause the blades 8 to rotate by a reference value.
- the input ratio is the smallest at the rotation angle of about +5°.
- the input ratio is the smallest at the rotation angle of about +10° at the position of the blade height ratio of 50% as illustrated in Fig. 12
- the input ratio is the smallest at the rotation angle of about +5° at the position of the blade height ratio of 75% as illustrated in Fig. 13 .
- the blade stagger angle ⁇ is preferably increased by causing the blades 8 to rotate on the + (positive) side to the maximum extent around the center in the blade height direction.
- Fig. 14 illustrates limit streamlines on the suction surfaces of the blades 8 according to the present embodiment, similarly to Figs. 9 and 10 . It is possible to ascertain from comparison between Figs. 10 and 14 that the radial direction component on the side of the roots 8a further decreases.
- the present embodiment has the following advantages.
- the blade stagger angle ⁇ 1 is caused to increase, that is, if the blades 8 are caused to rotate such that the shortest distance from the leading edge 8c and the trailing edge 8d to the adjacent blade 8 becomes short, the blades 8 are directed in a direction in which the blades 8 do not work, and the pressure thus decreases.
- the blade attachment angle ⁇ 1 is caused to locally increase such that the amount of change from the distribution that substantially linearly increases from the side of the roots toward the side of the tips of the blades 8 has the maximum value at the center position of the blade height with reference to the distribution. It is thus possible to optimize the pressure distribution on the blade surfaces in the radial direction, to reduce required input to the propeller fan 5, and thereby to improve performance.
- the present invention is not limited thereto and can be used not only for the blade in the first embodiment but also for blades with other shapes.
Abstract
Description
- The present invention relates to a propeller fan and an outdoor unit for an air conditioner provided with the same.
- For outdoor devices of air conditioners, propeller fans are used to blow air to outdoor heat exchangers. A propeller fan with a sickle shape in which blades are inclined forward in a rotation direction as disclosed in
Patent Literature 1, for example, has been proposed in order to reduce input or reduce noise. - [PTL 1]
the Publication of Japanese Patent No.4467952 - However, an outdoor heat exchanger is disposed on a side upstream of a propeller fan in an outdoor device of an air conditioner, it is not possible to cover a leading edge side of blades with a bellmouth due for a reason of disposition of the outdoor heat exchanger, and a configuration in which only a trailing edge side of the blades is covered with the bellmouth is employed. This leads to complicated flow field in which a flow from a tip side of the blades in a radial direction to the inner side in the radial direction and a flow in an axial direction parallel to a center axial line from the side upstream of the blades are present together. Thus, design of the propeller fan alone, that is, design that takes only the flow in the axial line direction into consideration does not lead to input reduction or noise reduction since the practical flow field is not taken into consideration, and it is thus not possible to sufficiently improve performance of the propeller fan.
- The present invention was made in view of such circumstances, and an object thereof is to provide a propeller fan capable of improving performance and an outdoor unit for an air conditioner provided with the same.
- A propeller fan according to an aspect of the present invention includes: a shaft portion that rotates around a center axial line; and a plurality of blades that have roots connected to an outer periphery of the shaft portion and extend in a radial direction, the blades have trailing edge side surface area increased regions and leading edge side surface area increased regions such that dimensions in an axial line direction parallel to the center axial line are larger on a side of tips than on a side of the roots in a case in which the blades are projected to a meridional plane including the center axial line, and the trailing edge side surface area increased regions are larger than the leading edge side surface area increased regions.
- The trailing edge side surface area increased regions are set to be larger than the leading edge side surface area increased regions to cause the trailing edge side to work more, and a flow in the radial direction is thus suppressed in the trailing edge side surface area increased regions. It is thus possible to curb peeling of a fluid from suction surfaces of the blades on the side of the roots, to uniformize flow amount distribution in a blade height direction (radial direction), and thereby to improve performance.
- For example, solidity obtained by dividing a chord length of the blades by a pitch is equal to or greater than 0.5 and equal to or less than 1.0, and is preferably equal to or greater than 0.6 and equal to or less than 0.95. Further, the solidity preferably reaches a minimum value at a midpoint position of the blade height.
- Also, a deflection angle obtained by subtracting an outlet angle from an inlet angle is set to substantially linearly decrease from the side of the roots to the side of the tips of the blades, for example.
- In addition, the dimension of the blades in the axial direction in a case in which the blades are projected to a meridional plane is set to be substantially constant from the roots (blade height ratio of 0%) to a blade height ratio of about 35% and substantially linear increase from the blade height ratio of about 35% to the tips (blade height ratio of 100%) .
- Further, in the propeller fan according to an aspect of the present invention, a blade stagger angle of the blades with respect to a direction of the center axial line locally increases such that an amount of change from distribution that substantially linearly increases from the side of the roots to the side of the tips has a maximum value at a center position of a blade height with reference to the distribution.
- If the stagger angle of the blades is increased, that is, if the blades are caused to rotate such that the shortest distance from a leading edge and a trailing edge of a blade to an adjacent blade becomes short, the blades are directed in a direction in which the blades do not work, and the pressure thus decreases. It is possible to optimize pressure distribution on the surfaces of the blades in the radial direction, to reduce required input to the propeller fan, and thereby to improve performance by locally increasing the blade stagger angle such that the amount of change from the distribution that substantially linearly increases from the side of the roots to the side of the tips of the blades has a maximum value at the center position of the blade height with reference to the distribution.
- Also, a propeller fan according to an aspect of the present invention includes: a shaft portion that rotates about a center axial line; and a plurality of blades that have roots connected to an outer periphery of the shaft portion and extend in a radial direction, a stagger angle of the blades with respect to a direction of the center axial line locally increases such that an amount of change from distribution that substantially linearly increases from a side of the roots toward a side of tips of the blades has a maximum value at a center position of a blade height with reference to the distribution.
- If the stagger angle of the blades is increased, that is, if the blades are caused to rotate such that the shortest distance from a leading edge and a trailing edge of a blade to an adjacent blade becomes short, the blades are directed in a direction in which the blades do not work, and the pressure thus decreases. It is possible to optimize pressure distribution on the surfaces of the blades in the radial direction, to reduce required input to the propeller fan, and thereby to improve performance by locally increasing the blade stagger angle such that the amount of change from the distribution that substantially linearly increases from the side of the roots to the side of the tips of the blades has a maximum value at the center position of the blade height with reference to the distribution.
- Moreover, an outdoor unit for an air conditioner according to an aspect of the present invention includes: the propeller fan according to any of the aforementioned propeller fans; a heat exchanger that is provided on a side upstream of the propeller fan; and a bellmouth that is provided so as to cause a leading edge side to be exposed and cover a trailing edge side of the propeller fan.
- It is possible to improve performance of the propeller fan by setting the trailing edge side surface area increased regions to be larger than the leading edge side surface area increased regions.
-
- [
Fig. 1 ]
Fig. 1 is a vertical sectional view of an outdoor unit for an air conditioner in a side view. - [
Fig. 2 ]
Fig. 2 is a vertical sectional view of the outdoor unit for an air conditioner in a plan view. - [
Fig. 3 ]
Fig. 3 is a front view of a propeller fan when seen in a direction of a center axial line. - [
Fig. 4 ]
Fig. 4 is a sectional view of two blades cut at a predetermined blade height position. - [
Fig. 5 ]
Fig. 5 is a graph illustrating a deflection angle with respect to a blade height ratio. - [
Fig. 6 ]
Fig. 6 is a graph illustrating a dimension of the blade in an axial direction with respect to the blade height ratio. - [
Fig. 7 ]
Fig. 7 is a graph illustrating distribution of a leading edge and a trailing edge of the blade in a case in which these are projected to a meridional plane. - [
Fig. 8 ]
Fig. 8 is a schematic diagram illustrating the blade projected to the meridional plane. - [
Fig. 9 ]
Fig. 9 is a simulation result illustrating limit streamlines in a front view of a suction surface of a typical propeller fan when seen in a direction of a center axial line. - [
Fig. 10 ]
Fig. 10 is a simulation result illustrating limit streamlines in a front view of a suction surface of a propeller fan according to a first embodiment when seen in a direction of a center axial line. - [
Fig. 11 ]
Fig. 11 is a graph illustrating an input ratio when a blade stagger angle is changed at a position of a blade height of 25%, according to a second embodiment. - [
Fig. 12 ]
Fig. 12 is a graph illustrating an input ratio when the blade stagger angle is changed at a position of a blade height of 50%. - [
Fig. 13 ]
Fig. 13 is a graph illustrating an input ratio when the blade stagger angle is changed at a position of a blade height of 75%. - [
Fig. 14 ]
Fig. 14 is a simulation result illustrating limit streamlines in a front view of a suction surface of a propeller fan according to the second embodiment when seen in a direction of a center axial line. - Hereinafter, a first embodiment according to the present invention will be described with reference to drawings.
-
Fig. 1 illustrates a sectional view of anoutdoor unit 1 for an air conditioner (hereinafter, simply referred to as an "outdoor unit 1") in a side view. Theoutdoor unit 1 is connected to one or a plurality of indoor units (not illustrated) with a refrigerant pipe. Apropeller fan 5 is disposed in acasing 3 of theoutdoor unit 1. Thecasing 3 has a substantially rectangular parallelepiped shape standing on a leg portion 4 placed on a floor surface. - The
propeller fan 5 is rotated about a center axial line L1 by amotor 7. Since the center axial line L1 extends in the horizontal direction, thepropeller fan 5 transversely blows air and causes the air to flow in the horizontal direction. - The
propeller fan 5 has ashaft portion 6 that is connected to themotor 7, is located on the side of the center axial line L1, and serves as a hub and threeblades 8 that are secured to an outer peripheral surface of theshaft portion 6. Note that the number ofblades 8 may be two, four, or more. Theblades 8 extend outward in the radial direction fromroots 8a connected to theshaft portion 6 towardtips 8b. - An
outdoor heat exchanger 9 is disposed on a side (the right side in the drawing) upstream of the air flow of thepropeller fan 5. Abellmouth 10 is disposed on a side (the left side in the drawing) downstream of the air flow of thepropeller fan 5. - The
bellmouth 10 is provided so as not to be present in the surroundings of aleading edge side 5a of thepropeller fan 5 and to cover the surroundings of a trailingedge side 5b of thepropeller fan 5. Such disposition in which theleading edge side 5a of thepropeller fan 5 is exposed from thebellmouth 10 is employed. -
Fig. 2 illustrates a vertical sectional view of theoutdoor unit 1 inFig. 1 in a plan view. As can be understood from the drawing, theoutdoor heat exchanger 9 is provided from aleft side surface 3a on one side to aback surface 3b of thecasing 3 and has a shape folded into an L shape. Since such anoutdoor heat exchanger 9 with the L shape is employed, an air flow passing through theoutdoor heat exchanger 9 and flowing into thepropeller fan 5 forms a complicated flow field. - A
machine chamber 12 in which a compressor that compresses a refrigerant and the like are disposed is provided on the side of theright side surface 3c of thecasing 3. Themachine chamber 12 and a space in which the air flows due to thepropeller fan 5 are sectioned by the sectioningwall 14. -
Fig. 3 illustrates a front view of thepropeller fan 5 when seen in a direction of the center axial line L1. In the drawing, the counterclockwise direction corresponds to a rotation direction R. Leading edges 8c and trailingedges 8d of theblades 8 have such shapes that the blades further stick out on the side of thetips 8b than on the side of theroots 8a. Also, theblades 8 have a sickle shape in which theleading edges 8c are inclined forward in the rotation direction R. - Solidity σ of the
blades 8 is equal to or greater than 0.5 and equal to or less than 1.0 and is preferably equal to or greater than 0.6 and equal to or less than 0.95. Also, the solidity σ reaches the minimum value at a midpoint position of the blade height. The solidity σ is a value obtained by dividing a chord length C by a pitch P that is a distance between theblades 8 in a section of each blade height, as inFig. 4 which schematically illustrates the blades 8 (σ = C/P). In the drawing, the rotation direction R of theblades 8 is directed downward, and the air flow is directed from the left to the right. Therefore, an inclination angle of theleading edges 8c with respect to the direction of the center axial line L1 is an inlet angle α1, and an inclination angle of the trailingedges 8d with respect to the direction of the center axial line L1 is an outlet angle α2, as illustrated in the drawing. - As illustrated in
Fig. 5 , a deflection angle Δα (= α1 - α2) obtained by subtracting the outlet angle α2 from the inlet angle α1 is set to substantially linearly decrease from the side of theroots 8a to the side of thetips 8b of theblades 8. In the drawing, the horizontal axis represents the blade height ratio while the vertical axis represents the deflection angle Δα. The blade height ratio is 0 (0%) at theroots 8a and is 1.0 (100%) at thetips 8b (the dimension of the direction of the center axial line L1). - As illustrated in
Fig. 6 , the dimension of theblades 8 in the direction of the center axial line L1 in a case in which theblades 8 are projected to a meridional plane is set so as to be substantially constant from theroots 8a (blade height ratio of 0%) to the blade height ratio of about 35% and to substantially linearly increase from the blade height ratio of about 35% to the tips (blade height ratio of 100%). In the drawing, the horizontal axis represents the blade height ratio while the vertical axis represents the axial width expressed in a non-dimensional manner with the diameter at thetips 8b of theblades 8. -
Fig. 7 illustrates distribution of theleading edges 8c and the trailingedges 8d of theblades 8 in a case in which theblades 8 are projected to a meridional plane, in the radial direction (horizontal axis) and the axial direction (vertical axis). As can be understood from the drawing, the axial width is larger on the side of thetips 8b than on the side of theroots 8a of theblades 8 as illustrated inFig. 6 . - Regions (leading edge side surface area increased regions S1) sticking on the side (the lower side in the drawing) upstream of the air flow is present from the side of the
roots 8a at which the position of theleading edges 8c in the axial direction is constant to the side of thetips 8b. Similarly, regions (trailing edge side surface area increased regions S2) sticking on the side (the upper side in the drawing) downstream of the air flow is present from the side of theroots 8a at which the position of the trailingedges 8d in the axial direction is constant to the side of thetips 8b. Also, the trailing edge side surface area increased regions S2 are set to be larger than the leading edge side surface area increased regions S1 (S2 > S1). - According to the present embodiment, the following advantages are achieved.
- Since the trailing edge side surface area increased regions S2 are set to be larger than the leading edge side surface area increased regions S1, the side of the trailing
edges 8d is caused to work more, and the flow in the radial direction is thus suppressed in the trailing edge side surface area increased regions S2. In other words, it is possible to direct the flow having a radial direction component illustrated by the solid line arrow to the horizontal direction (the direction of the center axial line L1) by reducing the radial direction component as illustrated by the dashed line arrow, as schematically illustrated inFig. 8 . It is thus possible to curb peeling of a fluid from the suction surfaces of theblades 8 on the side of theroots 8a, to uniformize flow amount distribution in the blade height direction, and thereby to improve performance. -
Figs. 9 and10 illustrate a simulation result of the present embodiment. The simulation was conducted under a condition of a positional relationship among thepropeller fan 5, theoutdoor heat exchanger 9, and thebell mouth 10 as illustrated inFigs. 1 and2 . In other words, this is not a simulation result of thepropeller fan 5 alone. The rotation direction R of theblades 8 inFigs. 9 and10 is clockwise turning (right turning) unlike inFig. 3 . -
Fig. 9 is a simulation result of a typical propeller fan in a comparative example. As can be understood from the drawing, it is possible to ascertain that limit streamlines illustrated on the suction surfaces of theblades 8 are directed in the radial direction. On the other hand, in thepropeller fan 5 to which the present embodiment is applied, the radial direction component of the limit streamlines illustrated on the suction surfaces of theblades 8 are reduced, and the limit streamlines are in the direction that substantially follows the rotation direction R, as illustrated inFig. 10 . The trend significantly appears in the regions of theroots 8a of theblades 8. - A second embodiment of the present invention will be described. The present embodiment was achieved by partially changing the shape of the blades in the first embodiment. Thus, description of matters that are common to those in the first embodiment will be omitted.
- The attachment angle of the
blades 8 described in the first embodiment is changed. As illustrated inFig. 4 , a blade stagger angle β1 is an angle formed between a tangential line L2 that is in contact with eachblade 8 cut at a predetermined position in the blade height direction on the side of the pressure surface (front surface side) and the direction of the center axial line L1. In the present embodiment, an intersection between a line connecting a gravity center of theblade 8 to the center axial line L1 with a shortest distance and a blade sectional surface cut at a predetermined position in the blade height direction was defined as a center position A, and performance in a case in which the blade stagger angle β1 was changed by causing theblades 8 to rotate about the center position A was compared. In regard to the rotation direction around the center position A, the counterclockwise turning inFig. 4 , that is, the direction in which theblades 8 are closed, in other words, the direction in which theleading edge 8c and the trailingedge 8d approach theadjacent blade 8 was defined as + (positive). Specifically, the cases in which theblades 8 were caused to rotate by ±10° at positions of the blade height ratios of 25%, 50%, and 75% were examined. -
Fig. 11 illustrates a case in which the blades are caused to rotate at the position of the blade height ratio of 25% to change the blade attachment angle β1. In the drawing, the horizontal axis represents the rotation angle of theblades 8 around the center position A while the vertical axis represents an input ratio of theblades 8, that is, a value obtained by dividing a power required to cause theblades 8 to rotate by a reference value. As can be understood from the drawing, the input ratio is the smallest at the rotation angle of about +5°. - On the other hand, the input ratio is the smallest at the rotation angle of about +10° at the position of the blade height ratio of 50% as illustrated in
Fig. 12 , and the input ratio is the smallest at the rotation angle of about +5° at the position of the blade height ratio of 75% as illustrated inFig. 13 . - It is possible to ascertain from
Figs. 11 to 13 that the blade stagger angle β is preferably increased by causing theblades 8 to rotate on the + (positive) side to the maximum extent around the center in the blade height direction. In other words, it is preferable to locally increase the blade stagger angle β1 of theblades 8 such that the amount of change from distribution that substantially linearly increases from the side of theroots 8a toward the side of thetips 8b of theblades 8 has a maximum value at the center position of the blade height with reference to the distribution. -
Fig. 14 illustrates limit streamlines on the suction surfaces of theblades 8 according to the present embodiment, similarly toFigs. 9 and10 . It is possible to ascertain from comparison betweenFigs. 10 and14 that the radial direction component on the side of theroots 8a further decreases. - The present embodiment has the following advantages.
- If the blade stagger angle β1 is caused to increase, that is, if the
blades 8 are caused to rotate such that the shortest distance from theleading edge 8c and the trailingedge 8d to theadjacent blade 8 becomes short, theblades 8 are directed in a direction in which theblades 8 do not work, and the pressure thus decreases. Thus, the blade attachment angle β1 is caused to locally increase such that the amount of change from the distribution that substantially linearly increases from the side of the roots toward the side of the tips of theblades 8 has the maximum value at the center position of the blade height with reference to the distribution. It is thus possible to optimize the pressure distribution on the blade surfaces in the radial direction, to reduce required input to thepropeller fan 5, and thereby to improve performance. - Note that although the second embodiment is used to adjust the shape of the blades in the first embodiment, the present invention is not limited thereto and can be used not only for the blade in the first embodiment but also for blades with other shapes.
-
- 1
- Outdoor unit (outdoor unit for air conditioner)
- 3
- Casing
- 3a
- Left side surface
- 3b
- Back surface
- 3c
- Right side surface
- 4
- Leg portion
- 5
- Propeller fan
- 5a
- Leading edge side
- 5b
- Trailing edge side
- 6
- Shaft portion (hub)
- 7
- Motor
- 8
- Blade
- 8a
- Root
- 8b
- Tip
- 8c
- Leading edge
- 8d
- Trailing edge
- 9
- Outdoor heat exchanger
- 10
- Bellmouth
- 12
- Machine chamber
- 14
- Sectioning wall
- A
- Center position
- C
- Chord length
- L1
- Center axial line
- L2
- Tangential line
- P
- Pitch
- R
- Rotation direction (of propeller fan)
- α1
- Inlet angle
- α2
- Outlet angle
- β1
- Blade stagger angle
- σ
- Solidity
Claims (4)
- A propeller fan comprising:a shaft portion that rotates around a center axial line; anda plurality of blades that have roots connected to an outer periphery of the shaft portion and extend in a radial direction,wherein the blades have trailing edge side surface area increased regions and leading edge side surface area increased regions such that dimensions in an axial line direction parallel to the center axial line are larger on a side of tips than on a side of the roots in a case in which the blades are projected to a meridional plane including the center axial line, andthe trailing edge side surface area increased regions are larger than the leading edge side surface area increased regions.
- The propeller fan according to claim 1, wherein a blade stagger angle of the blades with respect to a direction of the center axial line locally increases such that an amount of change from distribution that substantially linearly increases from the side of the roots to the side of the tips has a maximum value at a center position of a blade height with reference to the distribution.
- A propeller fan comprising:a shaft portion that rotates about a center axial line; anda plurality of blades that have roots connected to an outer periphery of the shaft portion and extend in a radial direction,wherein a blade stagger angle of the blades with respect to a direction of the center axial line locally increases such that an amount of change from distribution that substantially linearly increases from a side of the roots toward a side of tips of the blades has a maximum value at a center position of a blade height with reference to the distribution.
- An outdoor unit for an air conditioner comprising:the propeller fan according to any one of claims 1 to 3;a heat exchanger that is provided on a side upstream of the propeller fan; anda bellmouth that is provided so as to cause a leading edge side to be exposed and cover a trailing edge side of the propeller fan.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2018103741A JP7150480B2 (en) | 2018-05-30 | 2018-05-30 | Propeller fan and outdoor unit for air conditioner provided with the same |
PCT/JP2019/020593 WO2019230582A1 (en) | 2018-05-30 | 2019-05-24 | Propeller fan and air conditioner outdoor unit provided with propeller fan |
Publications (3)
Publication Number | Publication Date |
---|---|
EP3798451A1 true EP3798451A1 (en) | 2021-03-31 |
EP3798451A8 EP3798451A8 (en) | 2021-05-19 |
EP3798451A4 EP3798451A4 (en) | 2021-11-03 |
Family
ID=68698358
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP19810828.4A Pending EP3798451A4 (en) | 2018-05-30 | 2019-05-24 | Propeller fan and air conditioner outdoor unit provided with propeller fan |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP3798451A4 (en) |
JP (1) | JP7150480B2 (en) |
WO (1) | WO2019230582A1 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN116050028B (en) * | 2023-03-30 | 2023-06-20 | 陕西空天信息技术有限公司 | Impeller blade determination method, computer-readable storage medium, and electronic device |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5396512A (en) * | 1977-02-01 | 1978-08-23 | Torin Corp | Axiallflow disc wheel |
JPS62265499A (en) * | 1986-05-13 | 1987-11-18 | Mitsubishi Heavy Ind Ltd | Axial fan with moving blade of variable |
JPH08284887A (en) * | 1995-04-11 | 1996-10-29 | Toyo Radiator Co Ltd | Fan |
EP0945625B1 (en) | 1998-03-23 | 2004-03-03 | SPAL S.r.l. | Axial flow fan |
JP2002048094A (en) | 2000-08-07 | 2002-02-15 | Komatsu Ltd | Fan |
JP2005121310A (en) * | 2003-10-17 | 2005-05-12 | Hitachi Ltd | Air conditioner |
JP4467952B2 (en) | 2003-11-10 | 2010-05-26 | 東芝キヤリア株式会社 | Propeller fan, outdoor unit for air conditioner using this |
JP5079063B2 (en) | 2010-08-25 | 2012-11-21 | 三菱電機株式会社 | Propeller, blower and heat pump device |
JP6132380B2 (en) | 2012-02-06 | 2017-05-24 | ミネベアミツミ株式会社 | Impeller structure of axial fan |
JP6048024B2 (en) * | 2012-09-18 | 2016-12-21 | ダイキン工業株式会社 | Propeller fan |
JP5980180B2 (en) * | 2013-08-08 | 2016-08-31 | 三菱電機株式会社 | Axial flow fan and air conditioner having the axial flow fan |
-
2018
- 2018-05-30 JP JP2018103741A patent/JP7150480B2/en active Active
-
2019
- 2019-05-24 WO PCT/JP2019/020593 patent/WO2019230582A1/en unknown
- 2019-05-24 EP EP19810828.4A patent/EP3798451A4/en active Pending
Also Published As
Publication number | Publication date |
---|---|
WO2019230582A1 (en) | 2019-12-05 |
EP3798451A8 (en) | 2021-05-19 |
JP2019206958A (en) | 2019-12-05 |
JP7150480B2 (en) | 2022-10-11 |
EP3798451A4 (en) | 2021-11-03 |
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